Elastohydrodynamic sliding bearings



Dec 1 'r. E. TALLIAN ETA!- ELASTOHYDRODYNAMIC SLIDING BEARINGS 2 Sheets-Sheet 1 Original Filed March 19, 1968 B wss DIMENSIONLESS SPEED V DIMENSIONLESS LOAD =L INVENTORSZ TIBOR E.TALL|AN BY -LEW|S B.SIBLEY WWW ATTYS.

Dec. 1,.1970 'r. E. TALLIAN EI'AL 3,544,177

ELAS'IOHYDRODYNAMIC SLIDING BEARINGS I Original Filed March 19, 1968 I 2 Sheets-Sheet 2 FIG. 3. i i i INVENTORSI TIBOR E. TALLIAN LEWIS B. SIBLEY WWW United States Patent 3,544,177 ELASTOHYDRODYNAMIC SLIDING BEARINGS Tibor E. Tallian, Newtown Square, and Lewis B. Sibley, Wayne, Pa., assignors to SKF Industries, Inc., King of Prussia, Pa., a corporation of Delaware Application Mar. 19, 1968, Ser. No. 649,762, now Patent No. 3,421,799, dated Jan. 14, 1969, which is a continuation-in-part of application Ser. No. 457,913, May 24, 1965. Divided and this application June 11, 1968, Ser.

Int. Cl. F16c 17/06 US. Cl. 308--73 8 Claims ABSTRACT OF THE DISCLOSURE A11 elastohydrodynamic sliding bearing comprising first and second relatively movable members having confronting bearing surfaces and at least one or a plurality of contact members between the confronting surfaces of a configuration to define a plurality of contact zones. A lubricant is provided between the bearing surfaces and the contact members so that when the members are rotated relative to one another while being in pressure-applying relation, a load-carrying uninterrupted elastohydrodynamic film is formed for a predetermined range of entrainment velocities of the members moving through the contact zones and for a predetermined range of loads and contact curvatures. It has been found that ranges of variables to produce an elastohydrodynamic film are given approximately by the following inequalities:

G1.6V0.7 a V where G is the material parameter, V is the entrainment veloclty, L is load, R is the equivalent radius of the contacting surfaces and a is the surface roughness of the surfaces in contact.

This is a divisional application of my prior copending application, Ser. No. 649,762 filed Mar. 19, 1968, for Elastohydrodynamic Sliding Bearings, and now Pat. No. 3,421,799 which in turn is a continuation-in-part of my prior application, Ser. No. 457,913, filed May 24, 1965, for Elastohydrodynamic Sliding Bearings and now abandoned.

The present invention relates to bearings and more particularly to a new and improved type of bearing designated as an elastohydrodynamic, variable viscosity sliding bearing.

In order to highlight the principle of operation of the elastohydrodynamic sliding bearing of the present invention and its advantages over conventional bearings, it is considered desirable to discuss briefly the principle of operation and other factors such as load-carrying capacity, accuracy, lubricant requirements and friction, wear and fatigue characteristics of conventional bearings. For purposes of this discussion, bearings may be classified broadly in three main divisions; that is, hydrodynamic sliding bearings, rolling bearings, and hydrostatic sliding bearings.

In the operation of conventional hydrodynamic sliding bearings, the bearing surfaces of the bearing members sliding on each other are rigid and the lubricant in the form of a film between the bearing surfaces, which is under hydrodynamic pressure generated by the motion of the bearing itself, serves to support the bearing surfaces in spaced relation to permit relative movement of the bearing members without wear. In hydrostatic fluid film bearings, the confronting surfaces of the bearing members are maintained in spaced relation by a fluid lubricant pressurized hydrostatically, from an outside source.

In roller bearings, the bearing surfaces rolling on each 3,544,177. Patented Dec. 1, 1970 other are elastic, and the lubricant is often present in the form of a film between the bearing surfaces. This film is under hydrodynamic pressure generated by the motion of the bearing itself. The hydrodynamic pressure is balanced by the elastic pressures arising from elastic deflection of the bearing surfaces. This interaction of hydrodynamic and elastic pressures is called an elastohydrodynamic condition.

The conventional hydrodynamic sliding bearing which may be characterized as a rigid isoviscous sliding device is in one simple form, a stationary sleeve which is used to support a rotatable member such as a shaft in a stationary housing. These sleeve bearings are generally employed in applications where radial space is an important factor since this type of bearing usually requires less radial space than many types of rolling bearings. Conventionally, a lubricant is provided between the interengaging cylindrical surfaces of the sleeve and shaft whereby upon relative rotation of the bearing surfaces, the hydrodynamic lubricant pressure builds up to support the shaft. In this type of bearing, there is a comparatively large contact area between the interengaging cylindrical bearing surfaces whereby the unit pressure is low and therefore, there is a comparatively small lubricant film pressure. Hence a relatively small supporting force or lifting force is provided by a given area of the lubricant film.

This type of bearing provides an accurate support at low loads and high speeds. However, as the load is increased, the film thickness drops and inaccurate shaft support results. Also, due to imperfections in the contacting bearing surfaces such as waviness, eccentricity and surface roughness, at high loads or under shock loading conditions, the lubricant film breaks down and the imperfections rub or engage, thereby resulting in wear and possible breakdown of the bearing. In this type of bearing the limited accuracies available in the large rigid bearing surfaces require relatively high values of film thickness to prevent rubbing of imperfections. However, the disadvantage of a thick film is that it requires great quantities of lubricant and as the film thickness varies in a variable speed and variable load application, the alignment accuracy of the supported members such as the shaft is affected. In terms of friction, hydrodynamic sliding bearing friction is low at medium speeds and high at high speeds and at zero speed. There is high wear at low speeds and substantially no wear at high speeds. The hydrodynamic sliding bearing does not shown appreciable fatigue.

Rolling bearings, which may be characterized as elastic variable-viscosity rolling devices, typically comprise inner and outer rings which are spaced apart to define an annular space for a plurality of rolling elements, either balls or rollers. These bearings require somewhat more radial space than hydrodynamic sliding types but much less axial space. They require small quantities of lubricant and the friction and wear factors are low over a wide speed range. However, the bearings eventually fail in fatigue. Rolling bearings provide extremely accurate support at low to medium loads and any speed. In these bearings, the total contact area between the balls or rollers and the rings is comparatively small and the unit pressures are extremely high and therefore, load-carrying capacity is limited by the ability of the bearing material to withstand high stress without premature fatigue.

The elasto-hydrodynamic films in rolling bearings are extremely thin, and their thickness varies very little with load due to the property of the lubricants used that their viscosity increases greatly under the high pressures in the contact areas of rolling bearing enabling the lubricant to carry high loads per unit area. The accuracy of a rolling bearing is limited under very high loads by the elastic deflections of the bearing surfaces at the small contact areas. In rolling bearings, the load-carrying capacity of a given bearing could be increased by enlarging the contact area between the rolling elements and the rings. However, the obvious limitation here isthat as the size of the rolling elements is increased to increase the contact area, the size of the bearing increases and the wasted space between the rollers also increase. In the third category, that is, the hydrostatic sliding bearings, the rotating shaft is supported or floated on a body of pressurized fluid lubricant, either gaseous or liquid. This arrangement requires a comparatively complicated and expensive lubricant feed system for the assembly. Furthermore, it is clear that difficulties in the lubricant feed system can prevent suitable operation of the hearing. The hydrostatic bearings are also rigid isoviscous sliding devices, and the limitations of accuracy in case of high or shock loads as well as high friction at high speed noted for hydrodynamic bearings apply to them also.

It has been found that if the confronting surfaces of a pair of bearing elements are of a given configuration to define a concentrated contact zone of a given geometry at a predetermined load and at a predetermined relative sliding movement of the bearing surfaces, that an uninterrupted load-carrying elastohydrodynamic film forms in the area of the contact zones to support the surfaces for optimum relative movement and the material of the bearing surfaces elastically deforms in the contact zones so that only a film thickness greater than the combined imperfections of the bearing surfaces need be provided to support the members for relative movement. Further, it has been found that in a bearing in accordance with the present invention, the accuracy of shaft positioning varies little over a wide load range; that is, the thickness of the elastohydrodynamic film remains substantially uniform regardless of load and thus, is insensitive to impact loading and provides extremely accurate support. For example, in accordance with one of the forms of elasto hydrodynamic sliding bearing of the present invention, the bearing comprises an outer ring having a generally cylindrical inner surface and an inner ring or shaft having a plurality of circumferentially spaced, outwardly directed arcuate projections in the form of spherical or convex protrusions which contact the bearing surface of the outer ring at a plurality of contact zones. In this bearing, assembly, when load is applied, the contact points (zones) elastically deform into relatively small, but distinct, contact areas so that when a lubricant is interposed between the contact 'areas and the rings are rotated relative to one another within a predetermined range of velocities, an uninterrupted load-carrying elastohydrodynamic film is formed at all of the contact areas providing a fluid film-supported hearing.

The elastohydrodynamic sliding bearing of the present invention has advantages over conventional rolling bearing assemblies. 'Ihe sliding bearing of the present invention has a greater load-carrying capacity for a given overall size because the contact conformity or osculation is outstanding or high in all planes.

The sliding bearing of the present invention is more compact radially than rolling bearing assemblies by reason of the fact that the rolling elements are eliminated, can be more simplified since no rolling elements andin several embodimentsno cage is-necessary and is also more economical to manufacture by reason of the fact that it has less parts, that is, no rolling elements, and in several embodiments, no cage.

In comparison with hydrodynamic bearings, the elastohydrodynamic bearing of the present invention requires a much less lubricant, wears less at low speeds, has greater load-carrying capacity, is more accurate at all speeds and loads, and ismore compact axially.

The elastohydrodynamic sliding bearings of the, present invention has several advantages over hydrostatic bearings. For example, in hydrostatic bearings, the rotating elements of the bearing ass mbly re suppo ted or floated on a body of pressurized fluid lubricant, either gaseous or liquid, and this requires a comparatively complicated and expensive lubricant feed system. No such pressurized lubricant supply is needed in the bearing of the present invention. The advantages of axial compactness and load independent accuracy listed in comparison with hydrodynamic sliding bearings also apply here.

The elastohydrodynamic sliding bearing of the present invention provides for load independent rigid shaft positioning due to thin films and high comformities at the contact areas and has a greater load-carrying capacity for a given size as compared to fluid film bearings because of the virtual independence of film thickness from load and for the same reason is'insensitive to impact loading.

The elastohydrodynamic sliding bearing has longer fatigue life under a given load than a rolling bearing of the same size because the pressures on the bearing material in the contacts will be lower due to the better conformity. The sliding bearing of the present invention has high accuracy of shaft positioning at all loads because contact deformations are small and the elastohydrodynamic supporting film is very thin. Moreover, in the elastohydrodynamic sliding bearing of the present invention, the lubricant requirement is small and thus the entire bearing assembly may often be lubricated for life at assembly, it being noted that in these cases there is no external lubricant supply problem in bearing assemblies made in accordance with the present invention. Furthermore, the elastohydrodynamic sliding bearing of the present invention can be made in embodiments suitable for carrying radial and thrust loads.

With the foregoing in mind, an object of the present invention is to provide a new type of elastohydrodynamic sliding bearing which is characterized by noval features of construction and arrangement, providing high loadcarrying capacity and good resistance to fatigue.

Another object of the present invention is to provide an elastohydrodynamic sliding bearing assembly which is of comparatively simple construction and which is easy and economical to manufacture.

Still another object of the present invention is to provide an elastohydrodynamic sliding bearing which is adapted for accurate support of parts in high precision applications.

These and other objects of the present invention and the various features and details of a bearing assembly constructed in accordance with the present invention are hereinafter more fully set forth with reference to the accompanying drawings, wherein:

FIG. 1 is a fragmentary view with parts broken away of an elastohydrodynamic sliding bearing in accordance with the present invention;

FIG. 2 is a view taken on line 2-2 of FIG. 1;

FIG. 3 is a fragmentary view with parts broken away of a second embodiment of elastohydrodynamic sliding bearing in accordance with the present invention;

FIG. 4 is a view taken on lines 44 of FIG. 3;

FIG. 5 is an enlarged fragmentary sectional view of one of the slug members of the bearing of FIG. 3;

FIG. 6 is a fragmentary view with parts broken away of a third embodiment of elastohydrodynamic sliding bearing in accordance with the present invention;

FIG. 7 is a view taken on lines 77 of FIG. 6;

FIG. 8 is a side elevational view with parts broken away of a fourth embodiment of sliding bearing in accordance with the present invention;

FIG. 9 is an enlarged sectional view taken on line 9-9 of FIG. 8;

FIG. 10 is a fragmentary perspective view of the hearing shown in FIG. 8; and

7 FIG. 11 is a chart of dimensionless load versus dimensionless speed with a series of lines representing film thickness for given lubricants.

The elastohydrodynamic sliding bearing of the present invention comprises in broad terms first and second re1atively movable members having confronting bearing surfaces and at least one or a plurality of contact members between the bearing surfaces of a configuration to define contact zones with the bearing surface of the other mem ber whereby when the members are moved relative to one another at a predetermined rate while they are in a predetermined pressure-applying relation, an uninterrupted elastohydrodynamic film is formed between the bearing members at the contact zones providing a fiuid film-supported sliding bearing. More specifically and with reference to the enclosed chart wherein load is plotted against rate of relative movement of the sliding bearing surfaces, the elastohydrodynamic film forms in the elastic region marked E at a given load range and range of movement relationship within that region whereby the minimum film thickness required to support the members may be very small as long as it is greater than the combined imperfections of the members at the contact zones and remains substantially constant even as load is increased considerably, so that for all practical purposes, the film thickness is insensitive to load.

Considering now more specifically the present invention, and with reference to FIGS. 1 and 2 thereof, there is illustrated an elastohydrodynamic sliding bearing assembly in accordance with the present invention. As illustrated in FIG. 1, the assembly includes a rotating member 60, for example a shaft, and a stationary member 62 having a generally annular face 64 confronting the axial end of the shaft member 60. The stationary member 62 has a central raised hub portion 66 and in the space between the face 64 and the axial end of the member 60 there is mounted a plurality of slugs 68 having spherical or otherwise convex end faces 70 confronting the member 60 and the face 64 of the member 62 respectively which engage the rotating member 60 and the :face 64 of the stationary member at contact zones 67 and 69 respectively. These slugs 68 can be maintained in predetermined spaced apart relation by means of a cage member 74 if desired.

This configuration is particularly convenient and economical to manufacture because both shaft and support plate have plane surfaces, and provides a pure thrust hearing which will not suffer interference from radial shaft loads.

By way of illustration, the chart shown in FIG. 11 is a plot applicable for a given contact material and lubricant, as defined by a given value of the material parameter G=7E1, where 'y is the viscosity pressure exponent of the lubricant in the equation ,u=p. 'yP with e the basis of natural logarithms, p pressure and and n absolute viscosities at pressure p and atmosphere, respectively. E is the reduced modulus of elasticity defined below. The chart gives dimensionless load versus dimensionless speed for elastohydrodynamic bearings and is divided into four zones, rigid R, transitional T, elastic E and mixed-lubricated M and shows a series of lines H designating dimensionless film thickness. In the rigid zone, the bearing surfaces are relatively rigid, since the hydrodynamic fluid film pressure are relatively small, and in the elastic zone the bearing surfaces are elastically deformed and lubricant viscosity is increased in the contact zone since the elastohydrodynamic fluid film pressures are relatively high. In the transitional zone T lubricant viscosity is increased, but elastic deformation is negligible. In the mixed-lubricant zone M film thickness does not suffice to separate all surface asperities and therefore only an incomplete film exists at the contact zone. The bearing according to this invention is intended to operate in the elastic zone but may, in many cases be safely operated in any of the other zones shown on the chart.

In the chart, dimensionless entrainment velocity is defined as:

where n equals viscosity of the lubricant at the contact mlet, U equals relative entrainment velocity of contact surfaces and is further defined as where V1 and V2 are the linear velocities of the surfaces in contact with reference to such contact, E equals reduced modulus of elasticity defined as with V1, V2 and E E the Poissons ratio and Youngs modulus of the two contacting bodies, and R is the equivalent radius of the contacting surface defined as 1 1 1 FC T E Dimensionless load is expressed by the equation,

where w is load. Film thickness is expressed by where h is minimum film thickness. As shown in the chart, the elastohydrodynamic film forms in the elastic region at a given load range and speed range relationship and the minimum elastohydrodynamic film thickness required to support the members may be very small as long as it is greater than the combined surface imperfections of the members at the contact zones, and remains substantially constant even as load is increased so that for all practical purposes, the film thickness is insensitive to load. The minimum film thickness required to support the members is designated on the chart by the line H It is noted that this line will vary on the chart depending on the characteristics of the contact surfaces at the contact zones.

In arranging for a bearing according to this invention to function as an elastohydrodynamic bearing, it is necessary that the lubricant film thickness (h be suificient by comparison to the composite surface roughness defined as where 0' Q are the r.m.s. surface roughnesses of the two surfaces in contact. This is accomplished by satisfying the Formula 1 below; in which all quantities are substituted in compatible units of measurement Gust 01 The benefits claimed for the bearing according to this invention are fully realized when it operates in the elastic region E of chart 22. This is accomplished by satisfying, in addition to Formula 1, also Formula 2 below, in which all quantities are substituted in compatible units of measurement L 1 z m= (2) However, the bearing in this invention can, in general, satisfactorily be operated in regions other than the elastic region B, and will, as a result of temporary changes in load, speed, viscosity and other operating parameters, at times operate in these other regions.

The bearing arrangement shown in FIG. 3 is similar to that shown in FIG. 1 and comprises a rotating member 80 and a stationary member 82. However, in the present instance the axial end face of the member 80 is provided with a conical portion 84 and the stationary member 82 has a circumferentially extending raised lip 86 adjacent its outer periphery defining an annular shoulder 87. A plurality of slugs having spherical or otherwise convex faces engage between the conical face 84, shoulder 87 and the face 83 of the stationary member 82 at contact zones 85 and 89 respectively and are spaced by a cage. If desired this assembly has a self-centering ability and also has the advantage over the previous embodiment that the slugs spin while the bearing rotates, thereby eliminating the formation of wear spots during startup.

The bearing assembly shown in FIGS. 6 and 7 is similar to that shown in FIGS. 1 and 2 and comprises a rotating member 90 having a flat axial end face 94 and a stationary member 92 having an annular face 96 confronting the axial end face of the member 90 and also having a central raised hub portion 97. However, in this embodiment the slugs 98 are doughnut shaped and engage the rotating member 90 and stationary member 92 at contact zones 93 and 95 respectively. The slugs can be maintained in predetermined spaced apart relation by means of a cage member 99 if desired. This embodiment provides line contact between slugs and bearing surfaces at the contact zones and provides a pure thrust bearing without radial load interference.

In the bearing arrangements illustrated in FIGS. 6 and 7 when the rotating member is rotated at a predetermined velocity and when it engages against the slugs, the contact zones between the slugs, the rotating member and the stationary member deform according to Hertzian law into very small, but distinct contact areas, and an. elastohydrodynamic film forms which supports the members for relative rotation.

Illustrated in FIGS. 8, 9 and is another embodiment of elastohydrodynamic sliding bearing in accordance with the present invention. The bearing assembly is generally designated by the numeral 100 and comprises inner and outer rings 102 and 104 respectively having confronting spaced apart faces 103 and 105 defining an annular space 107 therebetween to receive a plurality of slug members 106. If desired, a cage may be provided to space the slugs 106. As best illustrated in FIG. 9, the outer ring 104 has at each axial end an inwardly directed lip or flange 109 defining a shoulder 111 limiting axial movement of the slugs 106. As illustrated, the face 105 of the outer ring is arcuate and convex in cross section for its entire circumferential extent. The face 103' of the inner ring is also arcuate and convex in cross section.

The external surface of each slug 107 is a portion of circular cylinder, with radius smaller than that of the surface 105. The internal surfaces of the slug 107 is a portion of a circular cylinder, with radius larger than that of the surface 103. The combination of the slugs with the rings produces point contact zones 113 and 115 with each other.

While particular embodiments of the present invention have been illustrated and described herein, it is not intended to limit the invention and changes and modifications may be made therein within the scope of the following claims.

What is claimed is:

1. A sliding bearing assembly comprising first and second relatively movable members having confronting first bearing surfaces, a plurality of contact members disposed between said confronting first bearing surfaces and slidably engaged therewith, each contact member having second bearing surfaces confronting said first bearing surfaces, said slidable engagement being such that each of said second bearing surfaces is constantly confronting only one of said first bearing surfaces, all of said first and second confronting bearing surfaces having GLBVOJ Lona V Lzgm 107 grs where G=the material parameter, V dimensionless entrainment velocity of the relatively moving bearing surfaces, L=dimensionless load, a=composite surface roughness of the bearing surfaces, R =the equivalent radii of the contacting bearing surfaces.

3. A bearing as claimed in claim 1 wherein said two planes are perpendicular to a plane tangent to said contact zones.

4. A bearing as claimed in claim 3 wherein one of said mutually perpendicular planes is formed by the intersection of the axis of rotation with a perpendicular line from said axis to a contact zone.

5. A bearing as claimed in claim 1 wherein there is point contact at the contact zones.

6. A sliding bearing comprising a rotating member, a stationary member, said member having confronting first bearing surfaces, one of said members having a central raised hub portion, a plurality of slug members having arcuate end faces defining second bearing surfaces confronting and engaging the first bearing surfaces of the rotating and stationary member, said slidable engagement being such that each of said second bearing surfaces is constantly confronting only one of said first bearing surfaces, all of said first and second confronting bearing surfaces having a relative curvature in two mutually perpendicular planes to define contact zones therebetween which are the sole support for load on the bearing, a lubricant between the slug members and bearing surfaces of the members, said lubricant forming a load-carrying uninterrupted elastohydrodynamic lubricant film at the contact zones at a predetermined range of rate of relative sliding movement of the members and at a predetermined range of loads thereby providing a fluid film-supported bearing.

7. A sliding bearing comprising a rotating member, a stationary member, one of said members having a conical portion defining a first bearing surface confronting a first bearing surface of the other member, a plurality of slug members having arcuate end faces defining second bearing surfaces confronting and engaging the first hearing surfaces of the rotating and stationary members, said slidable engagement being such that each of said second bearing surfaces is constantly confronting only one of said first bearing surfaces, all of said first and second confronting bearing surfaces having a relative curvature in two mutually perpendicular planes to define contact zones therebetween which are the sole support for load on the bearing, a lubricant between the slug members and bearing surfaces of the members, said lubricant forming a load-carrying uninterrupted elastohydrodynamic lubricant film at the contact zones at a predetermined range of rate of relative sliding movement of the members and at a predetermined range of loads thereby providing a fluid film-supported bearing.

8. A bearing as claimed in claim 6 wherein the slug members are doughnut shaped.

References Cited UNITED STATES PATENTS Coppage 308-219 Pickin 308-219 X Simler 308-174 Neeley 308-172 Scribner 308-73 Orshansky 308-73 Sperisn 308-73 Hill 308-73 FOREIGN PATENTS 5/ 1956 Great Britain 308-202 6/1926 Great Britain 308-73 OTHER REFERENCES German printed application 1,052,753, March 1959, Eberle. 

